Multi-port fluid valve and method

ABSTRACT

A multi-port valve is disclosed having a ball bearing support system for a stator/rotor/valve stem assembly within a valve housing. Slipper seals or alternatively, poppet seals, connect a plurality of apertures situated in the rotor and a plurality of apertures situated in the adjoining stator so that a common central fluid receiving channel of the stator can be connected to a peripheral fluid delivery channel of the stator via a transfer channel in the rotor. The valve assembly provides a durable, virtually leak-proof system for delivery of a variety of fluids through the same delivery channel.

This application claims benefit of provisional application Ser. No.60/122,148 filed Feb. 26, 1999.

BACKGROUND OF THE INVENTION

1. Field of the Invention

This invention relates generally to valves. More particularly, theinvention relates to valves having multiple ports.

2. Description of Related Art

Valve assemblies having multiple ports have existed for many years andhave been used in a wide variety of applications. One such applicationis the use in dental medicine. A device known as a tooth de-scaler isused to remove plaque build-up on teeth. The device uses ultrasonicwaves to effectuate the plaque removal.

While the device is being used, a stream of fluid is drawn into a smallhose attached to the tip of the de-scaling device where the fluid exits.The fluid is used to wash away any loosened plaque. Such toothde-scaling devices are designed to allow for three different fluidoptions. One option is regular tap water. A second option isbi-carbonate water. A third option is fluoride-fortified water.

Selection of the fluid source is accomplished by a multi-port valvewhich is required to handle pressures of approximately 65 psi which is atypical pressure at which tooth de-scaling devices are operated. Theneed to be able to shift quickly from one fluid option to another posesa number of problems.

One problem relates to the leakage of air from the multi-port valve.This is a problem that is common to most multi-port valves. The key isto limit the leakage to less than one bubble per second to achieve whatis known as “Bubble tight” operation when the valve ports are pluggedand the valve is submerged and pressurized. Some designs, for example, aconical valve and conical valve seat design, do not sufficiently seal tominimize bubble production. As a result, an undesirable hissing soundemanates from such a valve assembly when exposed to fluid pressures inthe 65 psi range.

It is therefore an object of the invention to provide a multi-port valvesystem that can minimize air leakage to no more than one bubble persecond. Another object of the invention is to provide a valve having a“miniature envelope” which meets or exceeds the criteria to receive ULapproval.

A still further object of the invention is to provide a bearing systemthat allows for effortless, maintenance-free rotation of the valve rotorwithin the valve housing.

SUMMARY OF THE INVENTION

The invention described herein employs a unique ball bearing supportsystem for a multi-port valve assembly. The valve apparatus also employsslipper seals to provide a virtually air-tight seal between a rotor andstator of the assembly so that a multitude of fluids can be selectivelytransported through the valve in an efficient cost effective manner.

The rotor/stem assembly is supported by ball bearings situated inannular chases provided in the valve housing and in a top end of therotor. Bores provided in the rotor receive the slipper seals which havethrough apertures to connect apertures in the rotor in fluidcommunication with apertures in the stator. Axial compression springsset within the rotor bores and within bores established in the slipperseals enhance the sealing effect by applying axial force to the slipperseals, forcing them into contact with the sealing face of the stator.

By rotating the rotor, a specific aperture in the stator is aligned witha fluid transmittal aperture/seal in the rotor. This aperture is influid communication with central fluid delivery apertures in the rotorand stator via a transverse channel. Alignment is accomplished by asystem of detents and detent channels positioned to allow for alignmentof the rotor apertures to the stator apertures. Stator apertures notaligned with the fluid receiving aperture are aligned with otherapertures in the rotor to provide a means to rapidly depressurize linesthat are either not in use or were in use just prior to the linepresently selected. A vent bore situated in a side wall of the housingprovides egress for any pressure buildup in unused lines.

The ball bearing support system coupled with the slipper seals providesa durable multi-port valve that can supply a selected fluid withoutcompromising the integrity of the seals or ease with which the fluidlines can be selected for delivery of the desired fluid. These and otherobjects and features of the present invention will be apparent from areview of the drawings and a reading of the following detaileddescription of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a plan view of a multi-port valve according to one embodimentof the invention.

FIG. 2 is a top view of a multi-port valve according to one embodimentof the invention.

FIG. 3 is a bottom view of a multi-port valve according to oneembodiment of the invention.

FIG. 4 is a top view of a rotor according to one embodiment of theinvention.

FIG. 5 is a sectional side view of a rotor according to one embodimentof the invention.

FIG. 6 is a top view of a stator according to one embodiment of theinvention.

FIG. 7 is a sectional side view of a stator according to one embodimentof the invention.

FIG. 8 is a side perspective view of a valve housing according to oneembodiment of the invention.

FIG. 8a is a top view of a valve housing according to one embodiment ofthe invention.

FIG. 9 is a bottom view of a valve housing according to one embodimentof the invention.

FIG. 10 is a side sectional view of a seal according to one embodimentof the invention.

FIG. 11 is a detent housing according to one embodiment of theinvention.

FIG. 12 is an end view of a detent housing according to one embodimentof the invention.

FIG. 13 is a side elevational view of a valve stem according to oneembodiment of the invention.

FIG. 14 is a side sectional view of a valve stem according to oneembodiment of the invention.

FIG. 15 is a sectional view of a key portion of a valve stem accordingto one embodiment of the invention.

FIG. 16 is a sectional view of a chamfered distal end of a valve stemaccording to one embodiment of the invention.

FIG. 17 is a top view of a valve stem according to one embodiment of theinvention.

FIG. 18 is a bottom view of a valve stem according to one embodiment ofthe invention.

FIG. 19 is a side sectional view of a bezel nut according to oneembodiment of the invention.

FIG. 19a is a bottom view of a bezel nut according to one embodiment ofthe invention.

FIG. 20 is a side perspective view of a center barb according to oneembodiment of the invention.

FIG. 21 is a side elevational view of a peripheral barb according to oneembodiment of the invention.

FIG. 22 is a bottom view of a peripheral barb according to oneembodiment of the invention.

FIG. 23 is a top view of a peripheral barb according to one embodimentof the invention.

FIG. 24 is a top view of a wave spring according to one embodiment ofthe invention.

FIG. 25 is a side view of a wave spring according to one embodiment ofthe invention.

FIG. 26 is a side view of a rotor/valve assembly according to oneembodiment of the invention.

FIG. 27 is a bottom view of a rotor/valve assembly according to oneembodiment of the invention.

FIG. 28 is a top sectional view of a portion of a valve assemblyaccording to one embodiment of the invention.

FIG. 29 is a top sectional view of a portion of a valve assemblyaccording to one embodiment of the invention.

FIG. 30 is a side view of a housing according to one embodiment of theinvention.

FIG. 31 is a side view of a housing according to one embodiment of theinvention.

FIG. 32 is a top view of a housing according to one embodiment of theinvention.

FIG. 33 is a bottom view of a housing according to one embodiment of theinvention.

FIG. 34 is a side view of a rotor/valve assembly bottom half accordingto one embodiment of the invention.

FIG. 35 is a top view of a rotor/valve assembly bottom half according toone embodiment of the invention.

FIG. 36 is a bottom view of a rotor/valve assembly top half according toone embodiment of the invention.

FIG. 37 is a side view of a rotor/valve assembly top half according toone embodiment of the invention.

FIG. 38 is a bottom view of a rotor/valve assembly top half according toone embodiment of the invention.

FIG. 39 is a sectional elevational view of a u-seal according to oneembodiment of the invention.

FIG. 40 is a bottom view of a u-seal according to one embodiment of theinvention.

FIG. 41 is a bottom view of a housing according to one embodiment of theinvention.

FIG. 42 is a bottom view of a bezel nut according to one embodiment ofthe invention.

FIG. 43 is a side view of a bezel nut according to one embodiment of theinvention.

FIG. 44 is a side view of a center barb according to one embodiment ofthe invention.

FIG. 45 is a top view of a center barb according to one embodiment ofthe invention.

FIG. 46 is a top view of gland nut according to one embodiment of theinvention.

FIG. 47 is a side view of a gland nut according to one embodiment of theinvention.

FIG. 48 is a side view of barb according to one embodiment of theinvention.

FIG. 49 is a top view of a barb according to one embodiment of theinvention.

FIG. 50 is a tip view of a stator axle according to one embodiment ofthe invention.

FIG. 51 is a side view of a stator axle according to one embodiment ofthe invention.

FIG. 52 is a top view of a stator according to one embodiment of theinvention.

FIG. 53 is a sectional view of a stator according to one embodiment ofthe invention.

FIG. 54 is a sectional view of a rotor/stator/barb/u-seal assemblyaccording to one embodiment of the invention.

FIG. 55 is a perspective view of a u-seal according to one embodiment ofthe invention.

FIG. 56 is a bottom view of a u-seal according to one embodiment of theinvention.

FIG. 57 is a sectional view of a u-seal according to one embodiment ofthe invention.

FIG. 58 is a side elevational view of a housing bottom half according toone embodiment of the invention.

FIG. 59 is a perspective view of a housing bottom half according to oneembodiment of the invention.

FIG. 60 is a top view of a housing bottom half according to oneembodiment of the invention.

FIG. 61 is a sectional view of a housing bottom half according to oneembodiment of the invention.

FIG. 62 is a side view of a housing bottom half according to oneembodiment of the invention.

FIG. 63 is a perspective view of a housing top half according to oneembodiment of the invention.

FIG. 64 is a side view of a housing top half according to one embodimentof the invention.

FIG. 65 is a top view of a housing top half according to one embodimentof the invention.

FIG. 66 is a sectional view of a housing top half according to oneembodiment of the invention.

FIG. 67 is a side elevational view of a housing top half according toone embodiment of the invention.

FIG. 68 is a side view of a valve stem portion of a valve stem/rotorassembly according to one embodiment of the invention.

FIG. 69 is a top view of a valve stem portion of a valve stem/rotorassembly according to one embodiment of the invention.

FIG. 70 is a perspective view of a valve stem of a valve stem/rotorassembly according to one embodiment of the invention.

FIG. 71 is another perspective view of a valve stem/rotor assemblyaccording to one embodiment of the invention.

FIG. 72 is a side view of a valve stem of a valve stem/rotor assemblyaccording to one embodiment of the invention.

FIG. 73 is a side view of a rotor of a valve stem/rotor assemblyaccording to one embodiment of the invention.

FIG. 74 is a perspective view of a rotor of a valve stem/rotor assemblyaccording to one embodiment of the invention.

FIG. 75 is another perspective view of a rotor of a valve stem/rotorassembly according to one embodiment of the invention.

FIG. 76 is a side view of a rotor of a valve stem/rotor assemblyaccording to one embodiment of the invention.

FIG. 77 is a top view of a rotor of a valve stem/rotor assemblyaccording to one embodiment of the invention.

FIG. 78 is a sectional view of a stator according to one embodiment ofthe invention.

FIG. 79 is a top view of a stator according to one embodiment of theinvention.

FIG. 80 is a side view of a valve stem/rotor assembly according to oneembodiment of the invention.

FIG. 81 is a top view of a valve stem/rotor assembly according to oneembodiment of the invention.

FIG. 81a is sectional view of a portion of a valve stem/rotor assemblyaccording to one embodiment of the invention.

FIG. 81b is a sectional view of a portion of a valve stem/rotor assemblyaccording to one embodiment of the invention.

FIG. 82 is a bottom view of a top portion of a housing according to oneembodiment of the invention.

FIG. 83 is a side view of a top portion of a housing according to oneembodiment of the invention.

FIG. 84 is a top view of a top portion of a housing according to oneembodiment of the invention.

FIG. 85 is a top view of a bottom portion of a housing according to oneembodiment of the invention.

FIG. 86 is a side view of a bottom portion of a housing according to oneembodiment of the invention.

FIG. 87 is an exploded view of a multiport fluid valve according to oneembodiment of the invention.

FIG. 87a is a side elevational view of an assembled multiport fluidvalve according to one embodiment of the invention.

FIG. 88 is a side elevational view of a bottom rotor and statorsub-assembly according to one embodiment of the invention.

FIG. 89 is a side elevational view of a multiport fluid valve accordingto one embodiment of the invention.

FIG. 90 is a side elevational view of a bottom rotor and statorsub-assembly according to one embodiment of the invention.

FIG. 91 is a side elevational view of a bottom rotor and statorsub-assembly according to one embodiment of the invention.

FIG. 92 is a side elevational view of a bottom rotor and statorsub-assembly according to one embodiment of the invention.

FIG. 93 is a side partial cutaway view of a bottom rotor and statoraccording to one embodiment of the invention.

FIG. 94 is a top view of a stator according to one embodiment of theinvention.

FIG. 95 is a sectional view of a stator according to one embodiment ofthe invention.

FIG. 96 is a bottom view of a stator according to one embodiment of theinvention.

FIG. 97 is a bottom view of a seal face according to one embodiment ofthe invention.

FIG. 98 is a side view of a seal face according to one embodiment of theinvention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring to FIG. 1, a multi-port valve according to one embodiment ofthe invention is shown. The valve comprises a housing 1, a valve stator2 that is sized to fit within housing 1, a bezel nut 3 that hasthreading (as shown in FIG. 19), situated about an inner annular wall ofbezel nut 3, a valve stem 4 that engages a rotor (shown in FIGS. 4 and5), situated within housing 1, a center barb 5 affixed to stator 2 viamated threading or permanent affixation, that provides a common channelfor fluids transported through the valve, and peripheral barbs (notshown) that provide fluid selectable channels for fluid transportedthrough lines (not shown) that are releasably secured to the peripheralbarbs.

Housing 1 has a radially extended base 6 to accommodate attachmentbores. As shown in FIGS. 3 and 9, optional pin locator bores 7 can beprovided to engage locator pins (not shown) projecting from a largerassembly to which the multi-port valve body is attached. Optional boreholes 8 can also be provided to accept mechanical fasteners (not shown).If threaded mechanical fasteners are used, bore holes 8 can be providedwith threading 9 extending axially along the portions of housing 1 thatdefine bore holes 8.

Radially extended base 6 has portions that define a large bore 10through which a portion of valve stem 4 exits. At a top end of housing1, external threading 11 is provided to matingly engage threading 82 ofbezel nut 3.

Housing 1 has further portions which define a vent bore 12 that allowsfor depressurization of peripheral channels not connected to the centralchannel. Situated in planes within the circumference of vent bore 12 area valve stem top annular plate 13, a wave spring 14 (shown in FIGS. 24and 25), an optional washer 14 a (shown in FIG. 87), and a bottom edgeof rotor 15.

Referring to FIGS. 8 and 8a, housing 1 has portions which define anannular housing chase 16 for containing ball bearings that support thevalve stem 4 and a rotor (not shown), features which are described inmore detail below. Extending axially upwardly from radially extendedbase 6 is annular wall 18 which defines aperture 10 and forms an innerannular wall of annular housing chase 16. Extending radially from a topedge of an outer annular wall of annular housing chase 16 is an annularchamfer 19 which has the function of facilitating loading of ballbearings 17 into annular housing chase 16.

Ball bearing 17 loading is accomplished efficiently by placing a plug(not shown), in aperture 10 and pouring ball bearings 17 into housing 1.Annular chamfer 19 cause ball bearings 17 to flow into annular housingchase 16. This process is continued until annular housing chase 16 has asupply of ball bearings 17 adequate to support valve stem 4 and theaforesaid rotor. In a preferred embodiment, annular housing chase 16 isnot filled to maximum capacity to allow free movement of the ballbearings and thus, free movement of valve stem 4 and rotor 15.

Ball bearings 17 may be made of steel or any engineering grade ofplastic or polymer. In a preferred embodiment, ball bearings 17 are madefrom Delrin® (Dupont), an acetyl-based resin.

Situated in a main annular wall 20 of housing 1 are a plurality ofdetent channels 21 which releasably arrest movement of rotor 15 withinhousing 1. The number and placement of detent channels 21 determine thenumber of positions and angular displacement of rotor 15 relative tostator 2.

To accommodate the dimensions of stator 2, main annular wall 20 is boredsuch that an annular shoulder 22 is formed at a top end of main annularwall 20. Annular shoulder 22 defines a top to end of detent channels 21.Alternatively, stator 2 can be downsized to fit within the dimensions ofmain wall 20 without further boring. The thickness of wall 20 can varyand is only limited in terms of minimal thickness to a thickness thatwill maintain the integrity of housing 1 after detent channels 21 areformed by boring or broaching.

If broaching is the procedure used to form detent channels 21, reliefchannel 23 is formed to allow an avenue of release for the cutter usedin the broaching process. If a boring process is used, formation ofrelief channel 23 can be eliminated.

To fix rotational and axial movement of stator 2 within housing 1, atleast one slot 24 is formed in a top edge of housing 1 to receive pins45 extending from a radial edge of stator 2. Preferably at least twoslots 24 are provided to stabilize stator 2 within housing 1.

FIGS. 31-33 show a molded version of housing 1, designated housing 100having optional pin locator bores 107 in a top surface that can beprovided to engage locator pins (not shown) projecting from a largerassembly to which the multi-port valve body is attached. Optional boreholes 108 can also be provided to accept mechanical fasteners (notshown). If threaded mechanical fasteners are used, bore holes 108 can beprovided with threading extending axially along the portions of housing100 that define bore holes 108.

Situated in a main annular wall 120 of housing 100 are a plurality ofdetent channels 121 which releasably arrest movement of rotor/valve stemassembly 115 within housing 100. The number and placement of detentchannels 121 determine the number of positions and angular displacementof rotor/valve stem assembly 115 relative to stator 200. Molded slots108 a are provided to allow for uniform cooling of the material used tomold housing 100.

To fix rotational and axial movement of stator 2 relative to housing 100if stator 2 is combined with housing 100, at least one slot 124 isformed in a top edge of housing 1 to receive pins 45 extending from aradial edge of stator 2. Preferably at least two slots 124 are providedto stabilize stator 2 within housing 100.

A main housing bore 119 is formed in housing 100 to receive inrotational engagement, rotor/valve stem assembly 115. Formed on a topsurface of housing 100 is aperture 110 that is sized to receive the mainvalve stem body 172 portion of rotor/valve stem assembly 115 thatproject out of housing 100.

Referring now to FIGS. 4 and 5, rotor 15 is shown which is sized to fitwithin housing 1 so that it can freely rotate within housing 1. Rotationof rotor 15 allows for the selection of ports contained within stator 2to be engaged for delivery of fluids. Rotor 15 has portions which definean annular rotor chase 25 for receiving ball bearings 17 which supportstator 2. An annular top exterior rotor wall 26 extends axially upwardlyfrom top face 27 of rotor 15. Top exterior wall 26 defines an outer wallof annular rotor chase 25 and functions to align stator 2 with rotor 15by mating with a portion of stator 2 that is sized to fit within theinner diameter of top exterior wall 26.

In one embodiment, top exterior wall 26 extends radially from side wall28 of rotor 15 to provide sufficient thickness to maintain the integrityof the wall 26 to perform the alignment function. In alternateembodiments, extension of top exterior wall 26 radially outwardly fromside wall 28 can be eliminated by downsizing the overall diameter ofstator 2 to fit within a smaller inner diameter of top exterior wall 26or by increasing the thickness of side wall 28 to match the outsidediameter of exterior wall 26.

Rotor 15 has portions which define a main rotor aperture 29 which issized to receive a portion of valve stem 4. Aperture 29 opens on abottom face 30 of rotor 15. Rotor 15 has further portions which definedetent housing apertures 31 which are situated in opposite ends of sidewall 28 and which open into main rotor aperture 29. Detent housingapertures 31 are sized to receive detent housing 60 as shown in FIGS. 11and 12.

In a preferred embodiment, detent housing 60 is a hollow cylindricaltube. Preferably detents 60 a (such as ball bearings shown in FIG. 11),and a detent spring 60 b are placed within detent housing 60. Detents 60a are free within detent housing 60 or are retained via crimping oradhesives. Detents 60 a are maintained at the ends of detent housing 60by detent spring 60 b situated within detent housing 60 between detents60 a. The detents 60 a are sized to releasably lock within detentchannels 21.

Rotor 15 has yet further portions which define a plurality of axialapertures 32 which run from top face 27 to main rotor aperture 29. Thenumber of axial apertures 32 is invariable and can be limited to one.All apertures 32 are in fluid communication with vent bore 12 whichallows for the depressurization of any channels that are not in use orhave been previously used. Venting can also be accomplished by utilizinga clearance around rotor 15 and housing 1 along with a clearance betweenrotor 15 and stator 2.

Situated in the approximate center of top face 27 is a main fluiddelivery bore 33. Main fluid delivery bore 33 is not in fluidcommunication with main aperture 29. Extending downwardly andconcentrically with main fluid bore 33 is fluid delivery counterbore 34which is sized to receive and engage a slipper seal as more fullydescribed below. Extending downwardly and concentrically with fluiddelivery counterbore 34 is fluid delivery aperture 35 which connectsfluid delivery bore 33 with a transverse fluid channel 36.

Extending downwardly from top face 27 and radially outwardly from fluiddelivery bore 33 is fluid conveying bore 37 which does not extendaxially to main aperture 29. Extending downwardly and concentricallywithin the diameter of fluid conveying bore 37 is fluid conveyingcounterbore 38 which is sized to receive and engage a fluid receivingslipper seal as more fully described below.

Extending downwardly and concentrically within the diameter of fluidconveying counterbore 38 is fluid conveying aperture 39 which connectsfluid conveying bore 37 with transverse fluid channel 36. Fluid deliverybore 33 and fluid conveying bore 37 are in fluid communication viatransverse fluid channel 36.

In one embodiment, transverse fluid channel 36 is formed by boringthrough side wall 28 at a position selected so that the walls oftransverse fluid channel 36 intersect the fluid delivery and conveyingapertures 35 and 39, respectively. To seal off transverse fluid channel36, a counterbore 40 is provided that is to concentric with channel 36.Counterbore 40 is sized to receive a plug that can be made from anysuitable material such as rubber or steel and can be shaped in the formof ball bearing 17.

Referring now to FIGS. 6 and 7, stator 2 is shown which has, in apreferred embodiment, a central aperture and a plurality of peripheralapertures to allow for the selective delivery of fluids via fluidcommunication with rotor 15. Stator 2 has a stator top face 41 a statorbottom face 42, both of which, in a preferred embodiment, are annular inshape and have diameters that are less than the diameter of a statorside wall 43 which, in a preferred embodiment has a diameter equal tothe outer diameter of top exterior wall 26 of housing 1. The junction ofstator bottom face 42 and stator side wall 43 form bottom shoulder 42 awhich centers stator 2 within top exterior wall 26. Stator bottom face42 is sized to fit within the inner diameter of top exterior wall 26.

The junction of stator top face 41 and stator side wall 43 form topshoulder 41 a which centers stator 2 within an aperture provided inbezel nut 3. Stator top face 41 is sized to fit within the diameter ofbezel nut aperture 80.

Provided in opposite ends of stator side wall 43 are pin bores 44 whichare sized to receive pins 45. Pins 45 when affixed to stator 2 extendradially from stator side wall 43. Pins 45 are sized to fit within thedimensions of slots 24 of housing 1. The combination of top exteriorwall 26, bottom shoulder 42 a, top shoulder 41 a, bezel nut aperture 80,slots 24 and pins 45 secure the location of stator 2 relative to housing1 and rotor 15 along the x, y and z axes.

Extending downwardly from stator top face 41 to a point short of statorbottom face 42 are a plurality of stator bores 46 which align with theaxial apertures 32 and fluid conveying bore 37 of rotor 15 when stator 2is placed on rotor 15. In a preferred embodiment, stator bores 46 havingthreading 47 to receive threaded barbs 65. In an alternate embodiment,barbs can be permanently fixed to stator bores 46 via methods such asbrazing.

As shown in FIGS. 21-23, threaded barbs 65 have portions which define athreaded barb aperture 66. To receive a hose (not shown), for fluidtransmission, threaded barbs 65 have an annular flange 67 that preventsretraction of the fluid conveying hose. To ease assembly of the hose tothreaded barb 65, a top end 68 of threaded barb 65 is chamfered.

To ensure an airtight seal, threaded barb 61 has an annular threadedbarb channel 69 into which an o-ring (not shown), is placed. Whenthreaded barb male threads 70 are mated to female threads 47 situated instator 2 by torquing threaded barb 61 into stator bore 46, treaded barb61 is torqued sufficiently tight to compress the o-ring to ensure anair-tight seal. Of course, the male to female threading can be reversedwith respect to barb 69 and stator 2. To aid torquing threaded barb 61,a radially extended portion 71 of a treaded barb side wall 72 isprovided. Radially extended portion 71 is shown as having anoctagon-shaped perimeter. The perimeter shape of radially extendedportion 71 can have any regular or irregular geometric shape. Analternate embodiment of threaded barb 65 in a non-threaded version 65 afor connection via brazing is shown in FIGS. 44 and 45.

Referring again to FIGS. 6 and 7, extending downwardly andconcentrically from stator bores 46 are fluid apertures 48 which are influid communication with axial apertures 32 and fluid conveying bore 37via slipper seals 51. The number of peripheral stator bores 46 and fluidapertures 48 establishes the number of possible fluid selections thatcan be made. The number of peripheral stator bores 46 is invariable andcan be limited to one. Preferably, one to eight peripheral stator bores46 are provided.

Extending downwardly from stator top face 41 to a point short of statorbottom face 42 and situated in the approximate center of stator top face41 is stator fluid delivery bore 49. Extending downwardly andconcentrically with stator fluid delivery bore 49 is stator fluiddelivery aperture 50 which is in fluid communication with fluid deliverybore 33 of rotor 15 via slipper seal 51. In a preferred embodiment,fluid delivery barb 61 (as shown in FIG. 20), is permanently fixed tostator fluid delivery bore 49 via brazing or other suitable method ofaffixation. In an alternate embodiment, stator fluid delivery bore 49can be provided with threading to receive a barb that has matedthreading like threaded barb 65 shown in FIGS. 21-23.

In a preferred embodiment, as shown in FIG. 20, fluid delivery barb 61has portions which define barb aperture 62. To secure a hose (notshown), delivery barb 61 has an annular flange 63. To ease assembly ofan appropriately sized hose to delivery barb 61, a top end 64 ofdelivery barb 61 is chamfered.

Referring now to FIG. 10, a slipper seal 51 is shown which functions asa bridge between rotor 15 and stator 2 to link, in fluid communication,the apertures and bores of rotor 15 with the apertures and bores ofstator 2. Slipper seal 51 is preferably cylindrical in shape with aslipper bore 52 extending downwardly from a slipper seal top face 53sized to receive an axial compression spring 54. Extending downwardlyfrom and concentrically with slipper bore 52 is through aperture 55which exits on a slipper seal bottom face 56. An annular o-ring groove57 is provided in a slipper side wall 58 for receiving an o-ring 59.

Slipper seal 51 is sized to fit within fluid conveying bore 33 and fluidconveying bore 37. Axial compression spring 54 is sized to fit withinfluid delivery counterbore 34 and fluid receiving bore 37 of rotor 15.O-ring 59 has an outside diameter that is sufficiently large to create afluid seal between rotor 15 and slipper seal 51. FIG. 89 shows a slipperseal embodiment used in conjunction with a rotor/valve stem assembly 115described in detail below.

Slipper seal 51 can be made from a variety of materials that have theability to conform to bottom face 42 of stator 2 to create a fluid sealwhile maintaining shape integrity when subjected to the torsional forcescreated by rotation of rotor 15. Examples of suitable materials include:high density graphites, silicon carbide and polymers. In a preferredembodiment, slipper seal 51 is comprised of Polymer Blend 45® (a blendof ultra high molecular weight polyethylene and teflon), fromPerformance Plastics (San-Ysidro, Calif.), which is more specifically apolytetrafluoroethylene based product that is preferred due to machiningease, durability characteristics and cost efficiency.

To ensure a leak-tight seal is created between slipper seal top face 53and bottom face 42 of stator 2, the adjoining surfaces can be smoothedby lapping the surfaces. However, it has been ascertained that thesurfaces need not be lapped if the appropriate materials are used andthe appropriate axial forces are generated by the system of springs inthe apparatus.

An alternative embodiment that substitutes a poppet assembly for aslipper seal assembly is shown in FIG. 88. In this embodiment, anactuator 400 is provided in fluid conveying bore 137. Actuator 400 canbe secured to rotor 119 via force fit, adhesive or with a screw425(shown in FIG. 90) that is threaded into a bottom of actuator 400through a bore formed from a top surface of bottom rotor/valve stemassembly 119 that is in communication with fluid conveying bore 137.Actuator 400 is secured to bottom rotor/valve stem assembly 119 beforerotor/valve stem assembly 119 is joined to top rotor/valve stem assembly118.

To ensure a tight seal between rotor/valve stem assembly 115 and stator200, an actuator o-ring bore 402 is provided in concentric relation withconveying bore 137 to receive an actuator o-ring 404. A rotor o-ringchannel 403 is provided about stator axle 153 to receive a rotor o-ring405 which ensures a good seal between stator 200 and rotor/valve stemassembly 115. At least two actuator channels 406 are provided in a topportion of actuator 400 that open into and are in fluid communicationwith an actuator chamber 408 that is in turn, in fluid communicationwith fluid conveying counterbore 138.

Situated in each stator bore 246 is a poppet 410. A poppet top end 412is preferably dome shaped and extends beyond a bottom surface 242 ofstator 200. Formed proximal to poppet top end 412 is poppet o-ringchannel 414 that is annular and sized to receive a poppet o-ring 416.Poppet 410 has a radially extending flange 418 that is situated adjacentto and forms a portion of poppet o-ring channel 416. A poppetcompression spring 420 is set between a bottom end of barb 65 and poppetflange 418. Poppet compression spring 420 biases poppet 410 so thatpoppet o-ring 416 is forced against a shoulder 411 of stator bore 246 sothat fluid flow between stator bore 246 and fluid conveying bore 137 isblocked when actuator 400 and poppet 410 are not in alignment. In aclosed position, poppet top end 412 comes into contact with a bottomface of rotor/valve stem assembly 115.

When actuator 400 and poppet 410 come into contact and alignment viarotation of rotor/valve stem assembly 115, actuator 400 which has a topend that is preferably flush with the bottom surface of rotor/valveassembly 115, overcomes the force generated by the poppet spring 420 sothat fluid communication between stator bore 246 and at least oneactuator channel 406 is achieved. Preferably, at least two actuatorchannels 406 are provided in actuator 400 to ensure fluid communicationin the event poppet 410 is radially displaced and blocks one of theactuator channels 406.

Another embodiment of the poppet form of seal is shown in FIG. 90.Actuator 400 is shown having a reduced diameter so that actuator 400does not occlude fluid conveying bore 137. Provided about actuator 400is actuator compression spring 430 that biases actuator o-ring 404 awayfrom a distal tip 400 a of actuator 400. Preferably distal tip 400 a istapered so that when actuator o-ring is biased toward distal tip 400 a,fluid communication between stator bore 246 and fluid conveying channel137 can be achieved about distal tip 400 a when actuator 400 and poppet410 are in alignment.

The presence of screw 425 occludes conveying aperture 139 and fluidconveying counterbore 138. To address the occlusion, auxiliary aperture138 a is provided to allow for fluid communication between transversechannel 136 and fluid conveying channel 137.

FIG. 92 shows a version of sealing the interfacing surfaces ofrotor/valve stem assembly 115 and stator 200.

Fluid conveying bore compression spring 430 a contacts a bottom shoulder431 formed between the junction of fluid conveying bore 137 and fluidconveying counterbore 138 and biases a conveying bore o-ring 404 aagainst stator 200. This provides an adequate radial and axial seal whenstator bore 246 is in alignment with fluid conveying bore 137. FIG. 93shows a combination of a slipper seal and o-ring to seal the interfacingsurfaces of rotor/valve stem assembly 115 and stator 200.

Turning to FIG. 91, a further poppet form of seal is shown where poppet410 is replaced with poppet ball 415. When not in alignment withactuator 400, poppet ball 411 seats against shoulder 411 due to the biasproduced by poppet spring 420.

Referring to FIGS. 39, 40, 56-57 and 89-93, a u-seal 450 is shown.U-seal 450 is preferably made of an elastomeric material that canwithstand the application of forces along different axes. It has beenfound that u-seal 450 provides a good seal for the juncture of reducedneck 156 and stator 200, a junction that is subject to axial as well asrotational and torsional forces during operation of the multi-port valveassembly.

U-seal 450 has a flat bottom u-seal surface 452 that defines a centralu-seal aperture 454. An inner annular u-seal wall 456 further definesu-seal aperture 454. An outer u-seal annular wall 458 is set at an anglerelative to u-seal surface 452 so that outer u-seal wall 458 expandsradially outwardly away from u-seal surface 452. Inner annular u-sealwall 456 expands radially inwardly away from u-seal surface 453 whichresults in outer u-seal wall 458 diverging from inner u-seal wall 456 toform an annular u-seal channel 460 that conforms to the shape of atrapezoid in cross-section. This configuration provides a seal that iscapable of withstanding multi-directional forces. However, an o-ring canbe substituted for u-seal 450 to provide a less effective but acceptableseal.

Referring now to FIGS. 13-18, valve stem 4 is shown. Valve stem 4 has avalve stem main body 72 that is sized to fit within large bore 10 ofhousing 1. It is important to the function of the apparatus that mainbody 72 can freely rotate within large bore 10.

Extending radially from main body 72 is valve stem top annular plate 13which is sized to fit snugly within main annular wall 20 of housing 1 sothat valve stem top annular plate 13 can rotate freely within housing 1.A bottom surface 73 of valve stem top annular plate 13 is chamfered toconform to annular chamfer 19 of housing 1. Bottom surface 73 is infrictional contact with ball bearings 17 which elevate valve stem 4 afraction of an inch above annular chamfer 19 to allow free rotation ofvalve stem 4.

Valve stem 4 has a top annular plate 74 which is sized to fit withinmain rotor aperture 29 so that top annular plate 74 can rotate freelywithin main rotor aperture 29. Top annular plate 74 has portions whichdefine detent housing channel 75. The combination of detent housingchannel 75 and detent housing 60 lock rotor 15 and valve stem 4 togetherso that the two parts of the valve assembly rotate in unison.

Extending from a bottom end of valve stem main body 72 is attachmentshaft 76 to which a variety of handles or knobs (not shown), can beattached to facilitate rotation of the rotor/valve stem assembly withinhousing 1. In one embodiment, as shown in FIGS. 14-18, attachment shaft76 can have a shaft chamfer 77 and a key extension 78 to lock a handleor knob into rotational unison with valve stem 4.

In a further embodiment, valve stem 4 and rotor 15 are combined into onecomponent as shown in FIGS. 26 and 27. Rotor/valve stem assembly 115 hasa main rotor/valve stem body 116 which has portions defining a detenthousing aperture 131 for receiving detent housing 60. A first annularrace 150 is formed on a top plate 151 which extends axially from a topsurface 152 of rotor/valve stem assembly 115. Top plate 152 reduces theoverall material needed for rotor/valve stem assembly 115.

Extending axially from top plate 151 is a preferably cylindricallyshaped integral stator axle 153 that is sized to receive in rotationalengagement, a corresponding aperture in a stator 200 described in moredetail below. Extending axially from stator axle 153 is reduced neckportion 156, the junction of neck portion 156 and stator axle 153forming axle shoulder 154. Formed and preferably radially centeredwithin stator axle 153 and neck portion 156 is common central rotorfluid delivery bore 135.

Central fluid delivery bore 135 is in fluid communication withtransverse channel 136 that extends radially from a preferably centerpoint of main rotor/valve stem body 116 and opens on the exterior radialwall of main rotor/valve stem body 116. A plug 140 is secured via forcefit, adhesive or other suitable method into the radial opening oftransverse channel 136.

Extending downwardly from top plate 151 and radially outwardly fromcommon central rotor fluid delivery bore 135 is fluid conveying bore137. Extending downwardly and concentrically within the diameter offluid conveying bore 137 is fluid conveying counterbore 138 which issized to receive and engage a fluid receiving slipper seal as more fullydescribed below.

Extending downwardly and concentrically within the diameter of fluidconveying counterbore 138 is fluid conveying aperture 139 which connectsfluid conveying bore 137 with transverse channel 136. Fluid deliverybore 135 and fluid conveying bore 137 are in fluid communication viatransverse channel 36.

Rotor/valve stem assembly 115 if formed from engineering grade plasticcan be formed from two molded portions, a top rotor/valve stem assembly118 and a bottom rotor/valve stem assembly 119. As shown in FIGS. 26,28, 29, 68-72, 80, 87 and 89, top rotor/valve stem assembly 118 combinesthe features of valve stem 4 with some of the features of rotor 15.

Top rotor/valve stem assembly 118 has a valve stem main body 172 that issized to fit within a large bore 110 of a housing 100 described in moredetail below. It is important to the function of the apparatus that mainbody 172 can freely rotate within large bore 110.

Extending radially from valve stem main body 172 is rotor/valve stemassembly annular plate 113 which is sized to fit snugly within a mainannular wall 120 of housing 100 so that rotor/valve stem assemblyannular plate 113 can rotate freely within housing 100. A bottom surface173 of annular plate 113 has an annular race 155 formed therein thatreceives ball bearings 17 which elevate rotor/valve stem assembly 115 afraction of an inch above a bottom inner surface of housing 100 to allowfree rotation of rotor/valve stem assembly 115.

Top rotor/valve stem assembly 118 has a post 174 which projects axiallyfrom a bottom surface of annular plate 113 and a cavity 174 formed inthe bottom surface of annular plate 113. Post 175 and cavity 175 matewith a corresponding cavity and post, respectively, formed on bottomrotor/valve stem assembly 119 as described below. A main valve cavity171 is formed in annular plate 113 and main body 172 when the assembly115 is molded from plastic material. Main valve cavity 171 enablesuniformity and proper heat dissipation when hot plastic is poured into amold.

Extending from a top end of valve stem main body 172 is attachment shaft176 to which a variety of handles or knobs (not shown), can be attachedto facilitate rotation of the rotor/valve stem assembly within housing100. In one embodiment, as shown in FIGS. 28, 29 and 37, attachmentshaft 176 can have a shaft chamfer 177 and a key extension 178 to lock ahandle or knob into rotational unison with rotor/valve stem assembly115.

As shown in FIGS. 26, 27, 34-36, 73-77, 80 and 81, bottom rotor/valvestem assembly 119 has all the features previously described forrotor/valve stem assembly 115 with the following additional features. Atop surface of bottom rotor/valve stem assembly 119 has a bottom post180 that projects axially from the top surface and a bottom cavity 181formed within the top surface. Bottom post 180 mates with cavity 175 andbottom cavity 181 mates with post 174 to ensure proper alignment of toprotor/valve stem assembly 118 to bottom rotor/valve stem assembly 119,each of which preferably form mating halves of detent channel 131. Ifmade of plastic and molded, as shown in FIG. 34, bottom rotor/valve stemassembly 119 can be formed without transverse channel 136 which canlater be formed by boring as is well known in the art. Similar to toprotor/valve stem assembly 118, if made by a molding process, optionalmain bottom cavity 182 can be formed in the mold (not shown), to ensureuniform cooling of molded bottom rotor/valve stem assembly 119.

As shown in FIGS. 52-54, 78, 79, 87, 87 a, 89, 92 and 93, a stator 200has, in a preferred embodiment, a central aperture and a plurality ofperipheral apertures to allow for the selective delivery of fluids viafluid communication with rotor/valve stem assembly 115. Stator 200 has astator top face 241 a stator bottom face 242, both of which, in apreferred embodiment, are annular in shape and have diameters that areless than the diameter of a stator side wall 243 which, in a preferredembodiment has a hexagonal shape. The hexagonal shape provides aninterference fit with a portion of housing 100 to lock into place andcenter stator 200 relative to rotor/valve stem assembly 115.

The junction of stator top face 241 and stator side wall 243 form topshoulder 241 a which centers stator 200 within an aperture provided in abezel nut 300. Stator top face 241 is sized to fit within the diameterof bezel nut aperture 80. The combination of hexagonally shaped sidewall 243, housing 100 having a hexagonally shaped cavity, top shoulder241 a and bezel nut aperture 380, secure the location of stator 2relative to housing 100 and rotor/valve stem assembly 115 along the x, yand z axes.

Extending downwardly from stator top face 241 to a point short of statorbottom face 242 are a plurality of stator bores 246 which align with thefluid conveying bore 137 of rotor/valve stem assembly 115 When stator200 is placed on rotor/valve stem assembly 115. Fluid communicationbetween stator bores 246 and fluid conveying bore 137 is accomplished bystator apertures 248 that preferably have a diameter less than thediameter of stator bores 246 and are formed on the bottom face 242oriented concentrically with stator bores 246. In a preferredembodiment, stator bores 246 having threading 247 to receive threadedbarbs 65. In an alternate embodiment, barbs can be permanently fixed tostator bores 246 via methods such as brazing.

Extending axially from top face 241 is central stator post 250. Formedwithin central stator post 250 is stator delivery bore 252 the walls ofwhich can have threads 254 to receive a central barb (not shown) havingmating threads. Situated at a bottom end of stator delivery bore 250 isneck receiving bore 256 that is sized to receive neck 156 of rotor/valvestem assembly 115. Directly below neck receiving bore 258 is a u-sealreceiving bore 260 that receives a u-seal 450 (described in more detailbelow). Directly below u-seal receiving bore 260 is stator axlereceiving bore 262 that is sized to receive in rotational engagement,stator axle 153. Stator delivery bore 252, neck receiving bore 256,u-seal receiving bore 260 and stator axle receiving bore 262 are all influid communication.

In an alternative embodiment, stator 200 has a large bore 270 formed onbottom face 242 that eliminates apertures 248. Secured to large bore 270is seal face 272. Seal face 272 provides a smooth, durable surface thatinterfaces with rotor/valve stem assembly 115. Seal face 272 can be madeof any material such as Teflon® impregnated nylon or Delrin®.

Formed in seal face 272 are seal face apertures 274 that are positionedto be in alignment with and in communication with stator bores 246. Sealface apertures 274 reduce the cross-sectional area of the statorconveying apertures which prevents o-rings used in place of slipperseals in some embodiments of the invention from herniating into thecross-sectional area of the bores in stator 200. Preferably three sealface apertures 274 are used for each stator bore 246. However, two sealface apertures 274 have also reduced o-ring herniation.

In another alternative embodiment, a non-integral stator axle 600 can beused in place of integral stator axle 153. Axle 600 is designed to bethreaded into the center of a top surface of rotor/valve stem assembly115 at a bottom end and inserted into a bore formed in the center ofbottom face 242 of stator 200. Axle 600 has a top axle bore 601 forreceiving a glan nut 620.

Glan nut 620 is preferably threaded and screwed into a threaded bore 635formed in the center of top face 241 of stator 200 to receive barb 65 ashown in FIGS. 44 and 45. A glan nut slot 622 is provided on a topflange 621 of glan nut 620. A stepped glan nut through bore 625 isprovided in glan nut 620 and sized to receive barb 65 a as shown in FIG.54. A u-seal 450 is provided between the interface of non-integralstator axle 600 and glan nut 620. Elastomeric or polymeric washers 627can be placed between barb 65 a and glan nut 620. An alternateembodiment of non-integral stator axle 600 is shown in FIGS. 48 and 49as stator axle 600 a that has a central through bore 601 a that providesfluid communication between stator 200 and rotor/valve stem assembly115.

Referring now to FIGS. 1,2,19 and 19 a, bezel nut 3 is shown which hasknurling 79 to ease torquing of bezel nut 3 onto housing 1. Torquing ofbezel nut 3 can be used to create axial forces that oppose the axialpreload generated by wave spring 14 and axial tension springs 54. Thisis accomplished by the dimensions of stator 2 and rotor 15 combined withthe height and threading of bezel nut 3. With the right combinationdimensions, the amount of torquing of bezel nut 3 onto housing 1 can beused to adjust and allow for the movement of rotor 15 within housing 1within a suitable psi range that is preferably between 0 to 150.However, the primary functions of bezel nut 3 is to retain stator 2 androtor 15 within housing 1 and to set the stack height of stator 2 androtor 15 to establish a suitable axial preload in conjunction with wavespring 14.

Bezel nut 3 has portions which define a bezel nut aperture 80 which issized to accept stator top face 41. Bezel nut 3 also has portions whichdefine a bezel nut main aperture 81 which is sized to matingly engagehousing 1 via bezel nut threading 82.

In an alternative embodiment, housing 1 and bezel nut 3 are replacedwith a two-piece housing 100 that is preferably molded as shown in FIGS.58-67 and 82-86. A top housing 100 a like other embodiments has optionalpin locator bores 107 in a top surface that can be provided to engagelocator pins (not shown) projecting from a larger assembly to which themulti-port valve body is attached. Optional bore holes 108 can also beprovided to accept mechanical fasteners (not shown). If threadedmechanical fasteners are used, bore holes 108 can be provided withthreading extending axially along the portions of top housing 100 a thatdefine bore holes 108.

Situated in a main annular wall 120 of top housing 100 a are a pluralityof detent channels 121 which releasably arrest movement of rotor/valvestem assembly 115 within top housing 100 a. The number and placement ofdetent channels 121 determine the number of positions and angulardisplacement of rotor/valve stem assembly 115 relative to stator 200.Molded slots 108 a are provided to allow for uniform cooling of thematerial used to mold housing 100.

A main housing bore 119 is formed in top housing 100 a to receive inrotational engagement, rotor/valve stem assembly 115. Formed on the topsurface of top housing 100 a is aperture 110 that is sized to receivethe main valve stem body 172 portion of rotor/valve stem assembly 115that project out of top housing 100 a. A radially extended housing tab109 is provided in on or in close proximity to a bottom end of tophousing 100 a to provide a means to align a bottom housing 100 bdescribed below.

As shown in FIGS. 58-62 and 85-86, bottom housing 100 b replaces bezelnut 3. Bottom housing 100 b has a top housing receiving bore forreceiving the exterior wall of top housing 100 a. A bottom end of tophousing 100 a is received in top housing receiving bore 190. Bottomhousing 100 b has a rotor bore 119 a defined by bottom housing innerwall 120 a that extends partially along the axial length of bottomhousing 100 b.

Bottom housing 100 b has a stator side wall receiving bore 192 that issized to receive in an interference fit, side wall 243 of stator 200. Astator receiving aperture 194 is formed on a bottom surface of bottomhousing 100 b to receive the top face 241 and acts as a stop withshoulder 142 a.

A housing slot 196 is provided in the wall of bottom housing 100 b toreceive housing tab 109. The combination of housing slot 196 and housingtab 109 allow for the alignment of top housing 100 a to bottom housing100 b and prevent relative rotational movement of the two components.Top housing 100 a is preferably secured to bottom housing 100 b withadhesive but can be configured to provide a force fit.

To assemble the multi-port valve, ball bearings 17 are introduced intoannular housing chase 16 using the procedure previously described. Next,valve stem 4 is inserted into housing 1 from the top of housing 1 untilseated on bearings 17. Wave spring 14 is set around top annular plate 74of valve stem 4. Rotor 15 with detent housing 60 and detents 60 a (ballbearings) pre-assembled in detent housing apertures 31 is placed withinhousing 1 so that main rotor aperture 29 engages top annular plate 74via insertion of detent housing 60 into detent housing channel 75.Slipper seals 51, preassembled with axial torsion springs 54 and o-rings59 are inserted into fluid delivery bore 33 and fluid conveying bore 37.Ball bearings 17 are then loaded into annular rotor chase 25. Next,stator 2 with, or without, delivery barb 61 and/or threaded barbs 65pre-assembled, is inserted into the top of housing 1 until coming intocontact with slipper seals 51 and ball bearings 17 which support stator2. Lastly, bezel nut 3 is torqued onto housing 1 until an appropriatetorque is achieved. An appropriate torque is achieved when valve stem 4can be rotated from one detent stop to another.

To operate the unit, fluid hoses are attached to the barbs and a knob orhandle is attached to the valve stem. Each detent channel isspecifically positioned so that at least one conveying channel isconnected via transverse fluid channel 36 to the delivery channel. Theconveying channels are positioned so that any channel not in use can bedepressurized rapidly after disengagement or engagement of one of theother conveying channels by the venting of pressure through the bottomof rotor 15 and out vent bore 12. The unique combination of the ballbearing support system with the slipper seals in a miniature multi-portvalve provides a durable, almost air tight valve that can be easilychanged from one fluid channel to another so that the fluid of choicecan be delivered on demand. It has been found that the multi-port valveassembly exhibits superior sealing characteristics such that a bubblerate of 1 bubble per minute is experienced at 55 psi, i.e., “leak-tight”performance.

It is to be understood that the present invention is by no means limitedto the particular constructions herein disclosed and/or shown in thedrawings, but also comprises any modifications or equivalents within thescope of the claims.

Having thus described our invention, what we claim as new and desire tosecure by United States Letters Patent is:
 1. A multi-port fluid valvecomprising: a valve housing having an inner housing wall defining afirst housing aperture in a first end having a first diameter, a secondhousing aperture in a second end having a second diameter smaller thanthe first housing aperture first diameter and an annular chase situatedabout said second housing aperture, a valve stem having an annularflange with a diameter sized to freely rotate within the first housingaperture and a valve stem shaft extending distally from the annularflange and dimensioned to fit within the diameter of the second housingaperture; a valve-free rotor having at least two rotor fluid receivingapertures and at least one rotor fluid delivery aperture wherein atleast one of the at least two rotor fluid receiving apertures isconnected to, and in fluid communication with, the rotor fluid deliveryaperture via a transverse channel; a stator having at least one statorreceiving aperture and at least one stator fluid delivery aperturewherein the stator is dimensioned to fit within the first housingaperture; and, at least two slipper seals having through apertureswherein the at least two slipper seals connect in fluid communicationthe at least one of the at least two rotor fluid receiving apertures tothe at least one stator receiving aperture and the at least one rotorfluid delivery aperture to the at least one stator fluid deliveryaperture.
 2. The valve of claim 1 further comprising a plurality of ballbearings dimensioned to roll within the annular chase.
 3. The valve ofclaim 2 further comprising a rotor annular chase formed in a top surfaceof the rotor.
 4. The valve of claim 1 wherein the rotor furthercomprises a fluid receiving aperture counter-bore concentric with the atleast one of the at least two rotor fluid receiving apertures and afluid delivery aperture counter bore concentric with the at least onerotor fluid delivery aperture, each counter-bore dimensioned to receiveone of the at least two slipper seals.
 5. The valve of claim 4 furthercomprising slipper seal o-rings wherein the at least two slipper sealshave annular slipper seal grooves for receiving the slipper sealo-rings, the slipper seal o-rings dimensioned to provide a seal betweenthe at least two slipper seals and the rotor counter bores.
 6. The valveof claim 4 wherein the at least two slipper seals comprise slipper sealbores formed on a bottom surface of each of the at least two slipperseals.
 7. The valve of claim 6 further comprising slipper seal springsdimensioned to fit within the slipper seal bores wherein the slipperseal springs bias the at least two slipper seals against a bottomsurface of the stator.
 8. A multi-port fluid valve comprising: a valvehousing having an inner housing wall defining a first housing aperturein a first end having a first diameter, a second housing aperture in asecond end having a second diameter smaller than the first housingaperture first diameter and an annular chase situated about said secondhousing aperture, a valve stem having an annular flange with a diametersized to freely rotate within the first housing aperture and a valvestem shaft extending distally from the annular flange and dimensioned tofit within the diameter of the second housing aperture; a rotor havingat least two rotor fluid receiving apertures and at least one rotorfluid delivery aperture wherein at least one of the at least two rotorfluid receiving apertures is connected to, and in fluid communicationwith, the rotor fluid delivery aperture via a transverse channel; astator having at least one stator receiving aperture and at least onestator fluid delivery aperture wherein the stator is dimensioned to fitwithin the first housing aperture; at least two slipper seals havingthrough apertures wherein the at least two slipper seals connect influid communication the at least one of the at least two rotor fluidreceiving apertures to the at least one stator receiving aperture andthe at least one rotor fluid delivery aperture to the at least onestator fluid delivery aperture; a plurality of ball bearings dimensionedto roll within the annular chase; and, a chamfered shoulder situatedbetween the inner housing wall and the annular chase and above theannular chase.
 9. The valve of claim 8 wherein the valve stem annularflange has a chamfered bottom surface configured to occupy a planeparallel to a plane occupied by the housing chamfered shoulder, thechamfered bottom surface being in contact with the plurality of ballbearings.
 10. The valve of claim 9 wherein the rotor further comprises arotor bore formed in a bottom surface of the rotor and at least onedetent aperture formed in a side wall of the rotor defining the rotorbore wherein the detent aperture opens into the rotor bore.
 11. Thevalve of claim 10 further comprising a detent fitted within the at leastone detent aperture.
 12. The valve of claim 11 wherein the housing hasat least one detent channel formed on the inner housing wall forreleasably receiving the detent.
 13. The valve of claim 12 wherein thevalve stem has portions configured to lock into the detent to lock thevalve stem and rotor in rotational engagement.
 14. A multi-port fluidvalve comprising: a valve housing having an inner housing wall defininga first housing aperture in a first end having a first diameter, asecond housing aperture in a second end having a second diameter smallerthan the first housing aperture first diameter and an annular chasesituated about said second housing aperture, a valve stem having anannular flange with a diameter sized to freely rotate within the firsthousing aperture and a valve stem shaft extending distally from theannular flange and dimensioned to fit within the diameter of the secondhousing aperture; a rotor having at least two rotor fluid receivingapertures and at least one rotor fluid delivery aperture wherein atleast one of the at least two rotor fluid receiving apertures isconnected to, and in fluid communication with, the rotor fluid deliveryaperture via a transverse channel; a stator having at least one statorreceiving aperture and at least one stator fluid delivery aperturewherein the stator is dimensioned to fit within the first housingaperture; at least two slipper seals having through apertures whereinthe at least two slipper seals connect in fluid communication the atleast one of the at least two rotor fluid receiving apertures to the atleast one stator receiving aperture and the at least one rotor fluiddelivery aperture to the at least one stator fluid delivery aperture; aplurality of ball bearings dimensioned to roll within the annular chase;a rotor annular chase formed in a top surface of the rotor; and, asecond set of ball bearings dimensioned to roll within the rotor annularchase.
 15. The valve of claim 14 wherein the second set of ball bearingscontact a bottom surface of the stator and allow for the free rotationof the rotor relative to the stator.
 16. The valve of claim 15 furthercomprising a bezel nut dimensioned to engage an outside wall of thehousing and having a central aperture for receiving the stator.
 17. Thevalve of claim 16 wherein the stator has an annular shoulder formed on atop surface of the stator dimensioned to fit within the bezel nutcentral aperture.
 18. A multi-port fluid valve comprising: a valvehousing having an inner housing wall defining a first housing aperturein a first end having a first diameter, a second housing aperture in asecond end having a second diameter smaller than the first housingaperture first diameter and an annular chase situated about said secondhousing aperture, a valve stem having an annular flange with a diametersized to freely rotate within the first housing aperture and a valvestem shaft extending distally from the annular flange and dimensioned tofit within the diameter of the second housing aperture; a rotor havingat least two rotor fluid receiving apertures and at least one rotorfluid delivery aperture wherein at least one of the at least two rotorfluid receiving apertures is connected to, and in fluid communicationwith, the rotor fluid delivery aperture via a transverse channel; astator having at least one stator receiving aperture and at least onestator fluid delivery aperture wherein the stator is dimensioned to fitwithin the first housing aperture; at least two slipper seals havingslipper seal bores formed on a bottom surface of each of the at leasttwo slipper seals and further having through apertures wherein the atleast two slipper seals connect in fluid communication the at least oneof the at least two rotor fluid receiving apertures to the at least onestator receiving aperture and the at least one rotor fluid deliveryaperture to the at least one stator fluid delivery aperture; slipperseal springs dimensioned to fit within the slipper seal bores whereinthe slipper seal springs bias the at least two slipper seals against abottom surface of the stator; and, a wave spring dimensioned to fitwithin the housing first aperture and situated between the rotor and thevalve stem flange wherein the wave spring biases the rotor away from thevalve stem the rotor having a fluid receiving aperture counter-boreconcentric with the at least one of the at least two rotor fluidreceiving apertures and a fluid delivery aperture counter boreconcentric with the at least one rotor fluid delivery aperture, eachcounter-bore dimensioned to receive one of the at least two slipperseals.
 19. The valve of claim 18 further comprising a rotor bore formedin a bottom surface of the rotor and a vent bore formed in a sidewall ofthe housing and in communication with the housing first aperture and therotor bore.
 20. The valve of claim 19 wherein a second of the at leasttwo rotor fluid receiving apertures is in fluid communication with therotor bore and the vent bore.
 21. A multi-port fluid valve comprising: avalve housing having an inner housing wall defining a first housingaperture in a first end having a first diameter, a second housingaperture in a second end having a second diameter smaller than the firsthousing aperture first diameter and an annular chase situated about saidsecond housing aperture; a valve stem having an annular flange with adiameter sized to freely rotate within the first housing aperture; arotor having a rotor annular chase formed on a top surface of the rotorand having at least two rotor fluid receiving apertures and at least onerotor fluid delivery aperture wherein at least one of the at least tworotor fluid receiving apertures is connected to, and in fluidcommunication with, the rotor fluid delivery aperture via a transversechannel; a stator having at least one stator receiving aperture and atleast one stator fluid delivery aperture wherein the stator isdimensioned to fit within the first housing aperture; at least twoslipper seals having through apertures wherein the at least two slipperseals connect in fluid communication the at lest one of the at lest tworotor fluid receiving apertures to the al least one stator receivingaperture and the at least one rotor fluid delivery aperture to the atleast one stator fluid delivery aperture; a plurality of ball bearingsdimensioned to roll within the annular chase; and, a second plurality ofball bearings dimensioned to roll within the rotor annular chase.